US10738873B2 - Device and method for vibration damping in conveyor drives - Google Patents
Device and method for vibration damping in conveyor drives Download PDFInfo
- Publication number
- US10738873B2 US10738873B2 US15/766,640 US201615766640A US10738873B2 US 10738873 B2 US10738873 B2 US 10738873B2 US 201615766640 A US201615766640 A US 201615766640A US 10738873 B2 US10738873 B2 US 10738873B2
- Authority
- US
- United States
- Prior art keywords
- drive system
- damper
- motor
- rocker
- stand
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active, expires
Links
- 238000013016 damping Methods 0.000 title claims description 14
- 238000000034 method Methods 0.000 title claims description 4
- 230000005540 biological transmission Effects 0.000 claims abstract description 21
- 229920001971 elastomer Polymers 0.000 claims description 16
- 239000000806 elastomer Substances 0.000 claims description 14
- 238000010168 coupling process Methods 0.000 description 13
- 238000005859 coupling reaction Methods 0.000 description 13
- 230000008878 coupling Effects 0.000 description 10
- 230000005484 gravity Effects 0.000 description 4
- 230000001360 synchronised effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- KUDUQBURMYMBIJ-UHFFFAOYSA-N 2-prop-2-enoyloxyethyl prop-2-enoate Chemical compound C=CC(=O)OCCOC(=O)C=C KUDUQBURMYMBIJ-UHFFFAOYSA-N 0.000 description 2
- 244000043261 Hevea brasiliensis Species 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 229920003052 natural elastomer Polymers 0.000 description 2
- 229920001194 natural rubber Polymers 0.000 description 2
- 239000005060 rubber Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- NLHHRLWOUZZQLW-UHFFFAOYSA-N Acrylonitrile Chemical compound C=CC#N NLHHRLWOUZZQLW-UHFFFAOYSA-N 0.000 description 1
- 239000005062 Polybutadiene Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229920002857 polybutadiene Polymers 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G27/00—Jigging conveyors
- B65G27/10—Applications of devices for generating or transmitting jigging movements
- B65G27/28—Applications of devices for generating or transmitting jigging movements with provision for dynamic balancing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02034—Gearboxes combined or connected with electric machines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02069—Gearboxes for particular applications for industrial applications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02069—Gearboxes for particular applications for industrial applications
- F16H2057/02073—Reduction gearboxes for industry
Definitions
- the invention relates to a drive system for conveyor drives, particularly in belt conveyors, and to a method for damping vibrations on the drive system of a conveyor drive.
- the company Nord Drivesystems advertises a modular drive system, in which the components can be combined to suit customer needs and requirements.
- the individual components are mounted on a carrier.
- One disadvantage is that in all drive systems vibrations occur, which may be caused by the interaction of the individual components. In particular, inadmissibly large vibrations can occur due to operating frequencies close to the natural system frequency.
- the operating frequency is derived from the rated speed of the asynchronous motor.
- the rated speed of the motor is obtained from the so-called motor synchronous speed and the motor slip (often in the range between 0.5 to 10%).
- the company brochure “Driving Greater Performance and Reliability—Belt Conveyor Drive Solutions” put out by Voith Turbo GmbH & Co. KG discloses drive systems designed according to customer requirements.
- the individual modules of the respective drive system are mounted on a carrier, also referred to as a rocker.
- the main components of a drive system are the motor, the turbo-coupling, also referred to as a hydrodynamic coupling, at least one connection clutch and the transmission.
- a drive system may comprise further components, such as a second connection clutch.
- An industrial brake may furthermore be provided, which serves to brake the drive unit in an emergency and/or as service and stop brake.
- the object of the invention is to develop a drive system in which the vibrations occurring are reduced.
- the aim is to reduce vibrations that occur perpendicularly to the orientation of the drivetrain.
- the invention relates to a drive system for conveyor systems.
- the term conveyor systems is in particular taken to mean belt conveyors and chain conveyors.
- the drive systems for conveyor systems comprise a motor, which is operatively connected to a transmission on the output side.
- the drive system is supported by means of a torque arm.
- the motor and the transmission are arranged axially in series, wherein further components, such as clutches, may be arranged between the motor and the transmission.
- a damper is arranged at the axial motor-side end of the drive system. It has been shown that this position of the damper is capable of effectively reducing the vibrations that occur in the drive system.
- the vibrations occurring at the motor-side axial end of the drive system are especially large, particularly in a drive system without dampers.
- the motor-side axial end is preferably at a distance from the torque arm. This distance constitutes a lever. This lever serves to enhance the action of the damper.
- the torque arm is preferably arranged in the area between the center of gravity of the motor and the center of gravity of the transmission of the drive system.
- the drive system is vertically supported by means of a torque arm.
- the vertical direction here is opposed to the weight acting.
- a horizontal direction is perpendicular to the axial extent of the drive system and to the vertical direction.
- a damper which is or can be tuned to different damper natural frequencies in at least two spatial directions.
- the operating frequency preferably corresponds to natural frequency of the system, the damper to the natural frequencies of the drive system in a vertical or horizontal direction perpendicular to the axial extent of the drive system.
- the natural frequencies of the drive system can be measured and also calculated using the masses, rigidities and the support points of the drive system.
- the damper natural frequency is tuned to the operating frequency of the drive system. Tuning is performed for maximum reduction of the vibration velocity.
- the operating frequency is obtained from the rated speed of the asynchronous motor.
- the rated speed of the motor is obtained from the so-called motor synchronous speed and the motor slip (often in the range between 0.5 to 10%, preferably 0.5 to 3%).
- a damper the total mass of which is less than 10%, preferably less than 5%, of the total mass of the drive system.
- the total mass of the damper does not include the elements that are needed in order to fix the damper to the drive system. Just by adding in this manageable mass, a considerable reduction in the vibrations can be achieved. At the same time the effect of the vibration damping of the damper is intensified due to its position and the operative lever principle. The lever is determined by the distance between the torque arm and the center of gravity of the damper mass.
- the damper has planar support in order to prevent tilting moments.
- Planar support is taken to mean support with at least three points of support lying in one plane.
- the plane defined in this way is also referred to as a supporting surface.
- the planar support serves to prevent the occurrence of tilting moments. It has proved advantageous here for the supporting surface to be arranged parallel to the axial extent of the drive system and the horizontal direction.
- a stand for planar support at the motor-side axial end of the drive system.
- the stand allows an arrangement of dampers available as standard components, so that the one damper natural frequency is operative in a vertical direction and the other, different damper natural frequency is operative in a horizontal direction of the drive system.
- the drive system comprises a rocker for supporting and fixing components of the drivetrain such as the motor and the transmission. It has proved advantageous for the damper to be arranged at the motor-side end of the rocker.
- the rocker at the motor-side end is provided with a stand.
- the stand comprises a planar horizontally and axially oriented stand base plate for planar support of the damper.
- the base plate affords an especially effective support for the damper. This support serves to prevent the occurrence of tilting moments in the damper. These tilting moments can occur particularly when the damper is connected to the drive system by only one fastener.
- the damper is supported in a vertical direction by a stay.
- This stay may support the damper directly, or the base plate of the stand may be supported by the stay. This stay contributes to the stability of the connection between the damper and the drive system.
- a damper which comprises a damping element, wherein the damping element is an elastomer having a hardness of 25 to 95 Shore, preferably a hardness of 70 to 80 Shore.
- damper in which the damping rate D lies in the range from 0.04 to 0.16, preferably 0.07 to 0.15.
- rocker for a drive system at an axial end having a stand for a planar support of a damper.
- the stand is preferably firmly connected to the rocker. Such a connection may be made by means of welding, bolting and/or riveting.
- FIG. 1 shows a drivetrain with damper and torque arm
- FIG. 2 shows a section through a torque arm
- FIG. 3 shows a torque arm
- FIG. 4 shows a damper at the axial end of the rocker
- FIG. 5 shows a rocker with a damper supported on one plane
- FIG. 1 shows a drivetrain 1 .
- a motor 3 is connected to the hydrodynamic coupling 9 via a connection clutch 5 .
- the hydrodynamic coupling 9 comprises at least an impeller and a turbine rotor.
- the impeller is connected to an input shaft of the hydrodynamic coupling 9 .
- the rotational movement of the impeller hydraulically drives the turbine rotor and hence the output shaft of the hydrodynamic coupling 9 .
- the hydrodynamic coupling 9 in particular the output shaft of the hydrodynamic coupling, is connected via a second connection clutch 7 to a transmission 13 .
- a brake 11 is arranged between the hydrodynamic coupling 9 and the transmission 13 .
- the brake 11 serves to stop the drive system in an emergency.
- the brake can also be used as a service and stop brake.
- the brake 11 is operatively connected to the hydrodynamic coupling 9 by a second connection clutch 7 .
- a connection clutch 14 arranged on the transmission output side constitutes an interface to the end pulley of a conveyor belt or a conveyor chain
- rocker 15 These components are arranged on a carrier 15 , hereinafter referred to as a rocker 15 , and are firmly fixed to the carrier 15 by fasteners 17 .
- the rocker 15 is supported by a torque arm 41 .
- the rocker 15 is provided with an end plate 37 .
- a damper 21 is arranged on the rocker 15 for damping vibrations. Vibrations of the rocker 15 are excited by the vibrations from the individual components transmitted to the rocker 15 . The static weights acting due to the mass of the individual components also act on the rocker 15 .
- the torque arm 41 is described in more detail with reference to FIGS. 2 and 3 .
- the torque arm 41 comprises an input element 43 .
- the input element 43 can be firmly connected to the rocker 15 .
- a fixed connection is produced by bolting.
- the input element 43 is supported on a first axis 45 , wherein an elastomer sleeve 53 is arranged between the input element 43 and the first axis 45 .
- the first axis 45 is firmly connected to connecting elements 47 on both sides by means of fasteners 49 .
- a second axis 51 is connected to the connecting elements 47 by means of fasteners 49 .
- This second axis 51 is likewise coaxially surrounded by an elastomer sleeve 53 , also referred to as a damping sleeve.
- the second axis is firmly connected to an output element 55 via this elastomer sleeve 53 .
- the output element 55 can be firmly connected to the surroundings. In the exemplary embodiment represented holes are provided, so that a bolt fixing is possible.
- the elastomer sleeves 53 assist in damping the vibrations of the rocker 15 .
- Natural rubber (NR/NK), and ethylene acrylate rubber (AEM) and acrylonitrile/butadiene rubber (NBR) have proved particularly suitable as material for the elastomer sleeves 53 .
- the damper 21 is intended to reduce vibrations of the drive system.
- the damper 21 is arranged at the motor-side axial end 19 of the rocker 15 , as shown in FIG. 4 .
- a damper marketed by the company ESM, for example, may be provided as damper
- Such a damper comprises a main mass 27 in the form of steel plates. These steel plates are connected via an elastomer to a centrally arranged sleeve.
- Such a damper 21 is a passive damper 21 . Passive dampers do not need an additional energy source and are excited to vibrate simply by the system to be damped.
- the damper 21 is provided with an elastomer as damping element, preferably having Shore A hardness of 70-80.
- a natural rubber (NR/NK) or an ethylene acrylate rubber (AEM) may be provided as elastomer.
- the centrally arranged sleeve constitutes an axial passage and is used for fixing the damper 21 .
- a bolt 25 is provided for fixing the damper 21 to the rocker 15 .
- the central sleeve and hence the bolt run in the Z-direction of the damper 21 .
- the X/Y plane is arranged perpendicular to the Z-direction.
- the damper acts in all three spatial axes and is thereby triaxial. It is only possible, however, to adjust the damper natural frequencies of the damper 21 in the Z-direction 30 independently of the X/Y-direction.
- Such dampers can be obtained as standard components, for example from the company ESM.
- the axial extent of the damper 21 is arranged in a horizontal direction. It would be desirable to be able to damp the vibrations occurring on the rocker in a horizontal direction and a vertical direction independently of one another. Although currently technically feasible, such dampers with damper natural frequencies adjustable in three axes of one another represent special models and are therefore expensive.
- FIG. 5 shows a further exemplary embodiment with a damper 21 previously explained in detail.
- the damper 21 in the exemplary embodiment represented in FIG. 5 is arranged with its Z-direction, Z-direction 30 of the damper 21 , in a vertical direction.
- the Z-direction 30 of the damper 21 in turn corresponds to the orientation of the axial extent of the central bore of the damper 21 .
- a stand 31 having a stand base plate 33 and stand stays 35 is provided for fixing the damper 21 .
- the stand base plate 33 is oriented horizontally. It is thereby possible to use a standard damper 21 with damper natural frequencies adjustable independently of one another in the Z-direction and the X/Y-direction 28 , 29 .
- the damper is arranged at the site of the maximum vibration amplitude, in order to exercise the maximum effect.
- the rocker will form its maximum vibration amplitude at the motor-side axial end.
- the damper is arranged at the motor-side axial end of the rocker 19 .
- the damper 21 is supported by means of a stand 31 .
- the stand 31 comprises a stand base plate 33 .
- the stand base plate 33 is arranged horizontally.
- Stand stays 35 serve to connect the stand base plate firmly to the rocker 15 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
motor | ||
synchronous | motor rated frequency | |
speed | motor rated speed | or operating frequency |
3600 | min∧−1 | 3240 min∧−1 | to 3582 min∧−1 | 54.0 Hz to 59.7 Hz |
3000 | min∧−1 | 2700 min∧−1 | to 2985 min∧−1 | 45.0 Hz to 49.8 Hz |
1800 | min∧−1 | 1620 min∧−1 | to 1791 min∧−1 | 27.0 Hz to 29.9 Hz |
1500 | min∧−1 | 1350 min∧−1 | to 1493 min∧−1 | 22.5 Hz to 24.9 Hz |
1200 | min∧−1 | 1080 min∧−1 | to 1194 min∧−1 | 18.0 Hz to 19.9 Hz |
1000 | min∧−1 | 900 min∧−1 | to 995 min∧−1 | 15.0 Hz to 16.6 Hz |
900 | min∧−1 | 810 min∧−1 | to 896 min∧−1 | 13.5 Hz to 14.9 Hz |
750 | min∧−1 | 675 min∧−1 | to 7461 min∧−1 | 11.3 Hz to 12.4 Hz |
-
- 1 drive system, drive package
- 3 motor
- 5 first connection clutch
- 7 second connection clutch
- 9 hydrodynamic coupling, turbo-coupling
- 11 brake
- 13 transmission
- 14 connection clutch
- 15 rocker
- 17 fastener
- 19 motor-side axial end of the rocker
- 21 damper
- 25 central bolt
- 27 main mass
- 28 X-direction of the damper
- 29 Y-direction of the damper
- 30 Z-direction of the damper
- 31 stand
- 33 stand base plate
- 35 stand stay
- 37 end plate
- 41 torque arm
- 43 input element
- 45 first axis
- 47 connecting element
- 49 fastener
- 51 second axis
- 53 damping sleeve, elastomer sleeve
- 55 output element
Claims (19)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015220030.2A DE102015220030A1 (en) | 2015-10-15 | 2015-10-15 | Apparatus and method for vibration damping in conveyor drives |
DE102015220030 | 2015-10-15 | ||
DE102015220030.2 | 2015-10-15 | ||
PCT/EP2016/073707 WO2017063920A1 (en) | 2015-10-15 | 2016-10-05 | Device and method for vibration damping in conveyor drives |
Publications (2)
Publication Number | Publication Date |
---|---|
US20180283523A1 US20180283523A1 (en) | 2018-10-04 |
US10738873B2 true US10738873B2 (en) | 2020-08-11 |
Family
ID=57133147
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/766,640 Active 2037-04-13 US10738873B2 (en) | 2015-10-15 | 2016-10-05 | Device and method for vibration damping in conveyor drives |
Country Status (8)
Country | Link |
---|---|
US (1) | US10738873B2 (en) |
EP (1) | EP3362707B1 (en) |
CN (1) | CN108138941B (en) |
AU (1) | AU2016338265B2 (en) |
DE (1) | DE102015220030A1 (en) |
PL (1) | PL3362707T3 (en) |
WO (1) | WO2017063920A1 (en) |
ZA (1) | ZA201801637B (en) |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB466755A (en) | 1935-12-03 | 1937-06-03 | Ewan Charles Caird | Improvements relating to driving means of belt, chain and like conveyors |
US2502564A (en) * | 1945-02-23 | 1950-04-04 | Electrolux Ab | Gearing housing |
DE1118693B (en) | 1959-09-26 | 1961-11-30 | Hauhinco Maschf | Conveyor belt drive station |
DE1148108B (en) | 1953-10-02 | 1963-05-02 | Clemens A Voigt | Vibration absorber made of a self-damped spring and a relatively small auxiliary mass connected to the spring |
US3338384A (en) * | 1965-07-13 | 1967-08-29 | Company Louisville Trust | Liquid mount tunable vibrating device for natural frequency vibrating conveyors |
DE2345935A1 (en) | 1973-09-12 | 1975-03-20 | Pohlig Heckel Bleichert | Drive for conveyor belt - has base frame mounted on torque and weight compensating elastic supports |
US4199271A (en) * | 1977-03-31 | 1980-04-22 | Wacker Werke Gmbh & Co Kg | Device for sealing V-belt and pulley in plate jarring devices |
US4356911A (en) * | 1980-07-18 | 1982-11-02 | Fmc Corporation | Linear drive unit for vibratory conveyor |
EP1693593B1 (en) | 2005-02-22 | 2008-09-17 | Franz Mitsch | Adjustable three-axis dynamic damper |
DE102011119045A1 (en) | 2011-11-22 | 2013-05-23 | Kurt Imren Yapici | Internal combustion engine and gear assemblage has vibration damper which comprises resonant frequency that coincides with resonant frequency of internal combustion engine and gear assemblage |
EP2727861A1 (en) | 2012-11-06 | 2014-05-07 | Takraf GmbH | Method for adjusting the position of the electric motor to the position of the drive drum of a direct drive for a belt conveyor assembly |
US8770389B2 (en) * | 2011-08-12 | 2014-07-08 | Tna Australia Pty Limited | Vibrator |
US10190670B2 (en) * | 2015-11-26 | 2019-01-29 | Gamesa Innovation & Technology, S.L. | Torque absorber for wind turbine gearboxes |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4209610C1 (en) * | 1992-03-25 | 1993-03-11 | Fa. Carl Freudenberg, 6940 Weinheim, De | |
US6617726B1 (en) * | 2002-05-02 | 2003-09-09 | Molon Motor & Coil Corporation | Motor gear box |
TWI240477B (en) * | 2004-09-29 | 2005-09-21 | Benq Corp | Motor vibration damping device |
CN103557314B (en) * | 2013-11-27 | 2015-10-28 | 于法周 | A kind of gear drive power mechanism |
CN103742593A (en) * | 2014-01-24 | 2014-04-23 | 哈尔滨工程大学 | Method for controlling anisotropic vibration of torsional vibration shaft system |
CN103851151B (en) * | 2014-03-15 | 2016-02-17 | 吉林大学 | Mine car electromagnetism power feeding shock absorber |
-
2015
- 2015-10-15 DE DE102015220030.2A patent/DE102015220030A1/en not_active Withdrawn
-
2016
- 2016-10-05 EP EP16781323.7A patent/EP3362707B1/en active Active
- 2016-10-05 PL PL16781323T patent/PL3362707T3/en unknown
- 2016-10-05 AU AU2016338265A patent/AU2016338265B2/en active Active
- 2016-10-05 US US15/766,640 patent/US10738873B2/en active Active
- 2016-10-05 WO PCT/EP2016/073707 patent/WO2017063920A1/en active Application Filing
- 2016-10-05 CN CN201680060028.1A patent/CN108138941B/en active Active
-
2018
- 2018-03-09 ZA ZA2018/01637A patent/ZA201801637B/en unknown
Patent Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB466755A (en) | 1935-12-03 | 1937-06-03 | Ewan Charles Caird | Improvements relating to driving means of belt, chain and like conveyors |
US2502564A (en) * | 1945-02-23 | 1950-04-04 | Electrolux Ab | Gearing housing |
DE1148108B (en) | 1953-10-02 | 1963-05-02 | Clemens A Voigt | Vibration absorber made of a self-damped spring and a relatively small auxiliary mass connected to the spring |
DE1118693B (en) | 1959-09-26 | 1961-11-30 | Hauhinco Maschf | Conveyor belt drive station |
US3338384A (en) * | 1965-07-13 | 1967-08-29 | Company Louisville Trust | Liquid mount tunable vibrating device for natural frequency vibrating conveyors |
DE2345935A1 (en) | 1973-09-12 | 1975-03-20 | Pohlig Heckel Bleichert | Drive for conveyor belt - has base frame mounted on torque and weight compensating elastic supports |
US4199271A (en) * | 1977-03-31 | 1980-04-22 | Wacker Werke Gmbh & Co Kg | Device for sealing V-belt and pulley in plate jarring devices |
US4356911A (en) * | 1980-07-18 | 1982-11-02 | Fmc Corporation | Linear drive unit for vibratory conveyor |
EP1693593B1 (en) | 2005-02-22 | 2008-09-17 | Franz Mitsch | Adjustable three-axis dynamic damper |
US8770389B2 (en) * | 2011-08-12 | 2014-07-08 | Tna Australia Pty Limited | Vibrator |
DE102011119045A1 (en) | 2011-11-22 | 2013-05-23 | Kurt Imren Yapici | Internal combustion engine and gear assemblage has vibration damper which comprises resonant frequency that coincides with resonant frequency of internal combustion engine and gear assemblage |
EP2727861A1 (en) | 2012-11-06 | 2014-05-07 | Takraf GmbH | Method for adjusting the position of the electric motor to the position of the drive drum of a direct drive for a belt conveyor assembly |
WO2014072331A1 (en) | 2012-11-06 | 2014-05-15 | Takraf Gmbh | Device for adapting the position of the electric motor to the position of the drive drum of a direct drive for a belt conveyor system |
US10190670B2 (en) * | 2015-11-26 | 2019-01-29 | Gamesa Innovation & Technology, S.L. | Torque absorber for wind turbine gearboxes |
Non-Patent Citations (1)
Title |
---|
Machine translation of DE 2345935 A1 obtained on Dec. 9, 2019. * |
Also Published As
Publication number | Publication date |
---|---|
PL3362707T3 (en) | 2021-06-14 |
CN108138941A (en) | 2018-06-08 |
ZA201801637B (en) | 2019-06-26 |
AU2016338265A1 (en) | 2018-05-10 |
DE102015220030A1 (en) | 2017-04-20 |
EP3362707B1 (en) | 2020-12-09 |
AU2016338265B2 (en) | 2021-02-25 |
US20180283523A1 (en) | 2018-10-04 |
CN108138941B (en) | 2021-08-17 |
WO2017063920A1 (en) | 2017-04-20 |
EP3362707A1 (en) | 2018-08-22 |
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